Heat engine



May 18 1965 T. Y. KORSGREN, sR 3,183,662

HEAT ENGINE Filed Feb- 18, 1963 4 Sheets-Sheet 1 Mm, Y, Y MM, ww .A2/4,) m 4v/A Ln mmf NNN m W Arrow/5v5. 7M

May 18, 1965 T. Y. KORSGREN, sR 3,183,662

HEAT ENGINE Filed Feb. 18, 1963 Arroz/VE Ys.

T. Y. KORSGREN, sR 3,183,662

May 1s, 1965 HEAT ENGINE 4 Sheets-Sheet 3 ,d l :Fr

Filed Feb. 18, 1963 May 18, 1965 T. Y. KORSGREN, SR

HEAT ENGINE 4 Sheets-Sheet 4 Filed Feb. 18, 1965 I NVENTOR.

7l!! /746L THEooo/E Y {M55/25AM@ BY ,Rafe/mama@ Z1/MUM W Arron/Essy Filed Feb. 18, 1963, Ser. No. 2S9,l98 12 Claims. (Cl. 60-24) The present invention relates to heat engines, and more particularly to heat engines of the type known generally as external combustion or hot air engines which employ a closed iluid system but otherwise function somewhat in accordance with an operating cycle known as the Stirling cycle.

With the advance of metallurgy and the development of materials capable of withstanding prolonged high temperatures and pressures, considerable interest and research has been initiated on engines of the type described because of their high efficiency, relatively silent operation and ability to utilize practically any type of fuel from natural gas to wood or peat.

In order to obtain high outputs from engines of this type, it is desirable to utilize fluids, such as hydrogen or helium, having high thermal conductivities and to utilize these fluids under high working pressures, sometimes as high as three thousand pounds per square inch. Also, since these engines are provided with a closed system containing fluid under high pressures and have heretofore utilized pistons to harness the output for driving crank mechanisms, severe problems of sealing the pistons to prevent the escape of the high pressure uid are encountered, particularly when large pistons are used. Moreover, engines of this type have reciprocating uid displacers which move in selected phase relationship with the pistons, and mechanism required for providing this movement is complicated and cumbersome with the result that diiliculty is encountered in obtaining engine balancing. Additionally, because of the time lag in heat flow to the system, control of engine speed and power output has been a difficult problem.

Accordingly, it is an object of the present invention to provide a new and improved external combustion engine utilizing a high pressure iluid in a closed system which overcomes or greatly reduces one or more of the aforementioned problems.

It is another object of the present invention to provide a new and improved engine of the type described above wherein working pistons are not required to derive a useful output from the closed system.

Still another object of the present invention is to provide a new and improved heat engine wherein the fluid itself is used to drive an output member directly and, thus, no crankshaft mechanism is required.

A further object of the present invention is the provision of a new and improved engine of the type described above wherein one or more pairs of closed system heat engines are utilized to drive a single output member.

Still a further object of the present invention is to provide a new and improved engine of the type described above wherein the engine output and speed can be readily controlled over a relatively wide range by means which independently control the speed and movement of fluid displacers within the system.

Yet another object of the present invention is to provide a new and improved engine of the type described above, wherein the output of the engine may be obtained from a separate member which is located remotely from the main part of the engine.

Another object of the present invention is to provide a new and improved engine of the type described above wherein a noncompressible fluid is used in place of pistons, with said fluid driving an output member.

United States Patent O fr* JSSZ Patented 18, 1955 Another object of the present invention is to provide a new and improved engine of the type described above wherein the output member is a fluid operated turbine or a reversely operated gear pump or other type of pump, and is used to drive electrical generating means which are sealed within the turbine or pump casing, thus eliminating the need for high-pressure rotary iluid seals.

Another object of the present invention is to provide a new and improved engine of the type described above wherein energy output from the turbine or pump means is coupled to a shaft by means of an electric clutch located exteriorly of the turbine or pump casing, thus eliminating high-pressure rotary fluid seals.

Another object of the present invention is to provide a new and improved engine of the type described above wherein particularly arranged fluid valve means are utilized to direct uid into and away from the turbine or pump members.

Further objects and advantages of the present invention will become apparent as the following description proceeds, and the features of novelty which characterize the invention will be pointed out with particularity in the claims annexed to and forming a part of this specification.

Briefly, the foregoing and other objects and advantages of the present invention are accomplished by the provision of one or more pairs of closed cycle heat engines, each engine of each pair including a chamber containing an operating uid under pressure and a liuid displacer movable therein. Fluid passages are provided to interconnect the ends of said chambers and there is provided in these passages an output member which is driven in response to the iiuid iiow in said passages. Means are also provided for moving the fluid displacers in phase opposition to one another so that fluid is circulated back and forth through the passages to drive the output member.

In one aspect of the invention, the output member comprises a rotary turbine and there are provided valve means in the passages for directing the fluid in the passages to the blades of the turbine in the proper manner. The fluid displacers can be driven directly from the turbine or in another embodiment independent means, such as a variable speed motor, is utilized to drive the uid displacers and thereby control the speed and output of the engine. A variable speed mechanical connection to provide a variable feedback may also be employed.

In one form of the invention the operating iluid is utilized to directly drive the output member, while in another a liquid, which is pressurized in response to the operating uid, is utilized to drive the output member.

In another form of the invention the output member is located remotely from the main part of the engine and fluid lines are utilized to direct the fluid from the engines to the output member.

Other aspects of the invention include the provision of an electrical generator which is positioned partly or entirely within the casing of the output member so that rotary high-pressure uid seals are unnecessary. In another instance the energy of the output member is coupled to a shaft by means of an externally located electrically operated clutch, again eliminating the need forv rotary high-pressure fluid seals.

For a better understanding of the present invention reference may be had to the accompanying drawings wherein:

FIG. 1 is a schematic illustration of one form of the heat engine of the present invention shown in one of its operating positions;

FIG. 2 is a schematic view similar to FIG. 1 showing the engine in another of its operating positions;

n, FIG. 3 is a schematic View of another embodiment of` the heat engine of the present invention utilizing a remotely positioned output member for driving an integral electrical generator andV having independent means for driving the fluid displacers inthe uid chambers;

FIG. 4 is a schematic view of yetanother embodiment of the heat engine of the presentinvention utilizing the operating fluid of the engine for directly driving the output member and showing an external electrically operated clutch member for coupling the output shaft to the output member;

FlG. 5 is an axial sectional view of a heat engine characterized by the features of the present invention which is illustrated schematically in FiG. l with the parts shown in the position of FIG. 2 taken substantially on line 5 5 of F IG. 7;

FIG. 6 is another axial sectional view similar to FIG- URE 5 but taken substantially along line 6 6 of FIG. 7;

FIG. 7 is a sectional view taken substantially along line 7 7 of FIG. 5, assuming that FIG. 5 shows the complete structure and showing certain portions in phantom;

FIG. 8 is a sectional View taken substantially along line 8 8 of FIG. 5, again assuming that FIG. 5 shows the complete structure and showing certain portions in phantom;

FIG. 9a is a sectional View taken substantially along y line 9er-#9a of FIG. 5, again assuming that FIG. 5 shows the complete structure;

FIG. 9b is a sectional View taken substantiallyalongv line 9]) 9b of FIG. 5, again assuming that FIG. 5 shows the complete structure; y v FIG. 10 is a sectional view taken substantially along line lm ltl of FIG. 5, again assuming that FIG. 5 shows the complete structure; n FIG. 11 is a top View taken substantially along line Il ll of FIG. 5, again assuming that FIG. 5 shows the complete structure;

FIG. l2is an enlarged fragmentary sectional view taken substantially along line 12-12 .of FIG. 9b; and

FIG. 13 is an enlarged fragmentary sectional view taken substantially along line 13 13 of FIG. 9a.

Referring now to the drawings and particularly to FIGS.

1 and 2, there is illustrated in schematic form one embodidesignated as 20L and 20R, respectively, which may be oriented to lie parallel to each other` as shown. Eachrof the engines 20L and ZtlR is identical and the description will be limited to only the heat engine 20L, while similar parts of the other engine will be given identical reference numerals.

The engine 7.9L includes a uid containing chamber 21 l which may take the form of a cylinder, but could be other than circular in cross-section if desired. Within the charnber 21 thereis provided uid displacer 22 which tits loosely therein and is reciprocally movable between an upper and a lower position, as illustrated in FIGS. 1 and 2 of the drawings. The displacers 22 in the chambers are phased so that when `one displacer is in the upper position the other one is in the lower position and vice versa.

The walls defining thechambers 21 are preferablyconstructed of astrong, light, high heat-strength and heat- 'resistant material, such as stainless steel; These chambers, moreover, are lled with a gaseous, compressible working fluid, such as hydrogen or helium, which fluid should have a high factor of heat conductivity and good flow characteristics. It is to be understood that other gases, such as the Freons, etc., might be used depending upon the operating temperature of the engine.

In order to provide la temperature differential between the upper and lower ends of the chambers 21,there is provided a'heat source 23 disposed adjacent the upper ends of these chambers. The heat source can be of many varied types, but in practice is of the fuel combustion type. Moreover, since the actualcombustion of the fuel does not take place within the chambers 2l practically any kind of fuel can be utilized from natural gas to wood or peat, etc. It is because ofy this feature that engines of this type have become known as -external combustion engines. It should be understood that other means can be used for maintaining a temperature differential between the opposite ends of the .chambers such as refrigerating one end to remove heat` from the'tiuid at the vcooled-ends of the chambers. V

For purposes of this description, a fuel source, such as natural gas, is used and supplies gas through a line 24 and control Valve 25 to burners Ziilocated"v adjacent the upper ends of the chambers 21. rThe upper ends of the chambers 21 are connected to the .lower ends thereof by means of a passage system dened'by conduit means 27. Portions of these conduit means adjacent the upper end of the chambers 2l are provided with fins 2S in order to aid in transfer of heat from theheat source such as burners 26 to theiiu'id within the conduit means 27 and, consequently, the upper ends of the chambersrZl'. The lower end of the conduit means 27 may be provided with tins 29 to cool the uid entering the lower ends of the chambers 21. With this arrangement the temperature of the Huid is raised when it is induced by the displacers to ow to the upper ends of chambers 21, and is lowered when itis induced to flow to the lower ends of these chambers. It shouldbernoted thatalthough the uid displacers 22 are loosely iittingwithinY the chambers 2l, as these displacers move up and down,fthe majority ofthe fluid in the chambers will pass from one end to the otherv thereof through the Aconduit means 27. Consequently, the pressure of the iiuid within the chambers 21 will alternately rise and fall depending on whether a major proportion of the duid is located at the heated end'or cooled end of the associated chamber as influenced by the displacer.

In order to improve the efliciency` of the engine, it has been found desirable to` place heat storing devices or regenerators 3Q in the conduit means .27.V Each heat storing device 3i) is generallyrconstructed of an insulated chamberhaving line `copper wool or lwire therein which rapidly picks up heat from the iluid leaving the top end of the associatedchamber 21,' Storing it until a reverse ow of fluid takes place and then the heat stored in the regenerator is given back to the Huid leaving the lower end of the chamber 21. In other words, .when the uid enters the top of either chamber 21 it becomes heated by virtue of the associated burner 26 and the total chamber pressure rises. When this uid is displaced `by the displacer 22 three things occur: (a) it gives up heat to its associated regenerator 36,(15) it moves'to the cool end 0f chamber 2l and (c) Vthe total chamber pressure falls.

In summary then, when the displacer 22 is near its lower position, the majority of the duid in that heat engine is at rthe top or hot end ofthe chamber 21 and is absorbing heat at high rate. As heat is absorbed by the iluid, the pressure in the chamber increases substantially. This increase is throughout the Whole chamber since the fluid displacer 22 is loosely fitting in this chamber and both ends of the chamber are interconnected by conduit means 27. When the iluid displacer 22V is near the upper end of its associated chamber 21, l[he majority of the uid is at the lower or cold end of the chamber` and the pressure throughout the whole chamber decreases substantially. Thus, as the fluid displacers 22 in each chamber 21 recriprocate back and forth, a high pressure is producedin one of the chambers While a low pressure is produced in the other chamber and vice-versa, producing an .alternating pressure differential or pressure pulse between the two chambers.

For the purpose of harnessing the energy available from is provided an output member 3.1 which may take the form' of a turbine 32 having a plurality of generally radially extending turbine blades 33. As illustrated the turbine 32 includes a disk-shaped member having an annular recess 31 with a curved bottom defined in the upper surface of the disk-shaped member. The blades 33 are preferably uniformly spaced within said annular recess 32. The turbine wheel 32 is mounted on a shaft 34- which is supported for rotation in a housing attached to the lower ends of the means defining the chambers 2l.

In order to accommodate a liquid or non-compressible fluid 36 which is used to drive the turbine wheel 32, the lower or cold ends of the chambers 21 extend downwardly for a distance below the level where the lower ends of the conduit means 27 communicate with the chambers 2l. Each of the chambers 21 is provided with an outlet passage 37 and an inlet passage 38 for directing the liquid iiuid 36 to and from the turbine wheel 32. The outlet passages 3'7 are provided with check valve means 39 for preventing flow from the turbine back into the chambers and the inlet passages 38 are provided with check valve means for preventing ow from the chambers 21 into the turbine 32. -In order that the discharge fluid from heat engine .261'J can be supplied to the chamber 21 of heat er1- gine 20K when the pressure in chamber 21 of heat engine "20k is decreasing and vice-versa, the passages 37 of each heat engine must be cross connected as indicated at 41 and similarly the passages 33 must be cross connected as indicated at 42. Preferably this is accomplished by chambers common to the passageways 37 in one case and 33 in the other case. This is specifically illustrated in the structural embodiment shown in FIGS. 5 to 13 of the drawings.

Considering now the operation of the external combustion engine 18 schematically illustrated in FIGS. l and 2 of the drawings, when the left-hand chamber 21 is in its low pressure phase and the right-hand chamber 2l is in its high pressure phase, 'as is the case in FIG. l, the fluid 36 fiows from the right-hand chamber 2l through the right-hand passageway 37 and associated check valve 39 inthe direction of the arrow to the output member specifically illustrated as a turbine 32. After giving up energy to drive the turbine 32, the fluid flows through the lefthand passage 38 and the left-hand check valve 4d int-o the lower end of the left-hand chamber 2l. Thus, the pressure of the gaseous fluid within the right-hand chamber 21 increases due to thermal increase and the pressure of the gaseous fluid in the left hand chamber decreases due to thermal decrease causing a flow of liquid from the higher pressured chamber to the lower pressure chamber.

A shor-t time later, the pressure in the left-hand chamber 21 becomes higher than that in the right-hand chamber 21 because of the heat absorption caused by movement of the displacers, and then fluid Hows from the lefthand chamber 2 through the left-hand passage 37 and the left-hand check valve 39 t-o the turbine 32. After giving up energy to drive the turbine, the fluid fiows out of the turbine through the right-hand passage 3S Iand right-hand check valve 40 into the right-hand chamber 21 in which the fluid is contracting.

Since the gaseous or working fluid in each chamber is expanded while under high pressure and temperature, and contracted while under low pressure and temperature, a work output is obtained to drive the output member designated as a turbine 32,

For the purpose of moving the uid displacers 22 as described above in proper phase relationship with one another, low friction means for converting rotary to reciprocating motion generally designated at 44 is provided. In a device built in accordance with the present invention thismeans comprised a rotary member 45 connected to turbine shaft 34. The rotary member 45 includes a circumferential groove 46 which groove is disposed at an angle of approximately sixty degrees with the longitudinal axis of the shaft 34. To provide a low friction cam device a ball bearing assembly has the inner race thereof disposed in groove d6 and is provided with a ring48 defining or secured to the outer race between which races the balls 5t) defining the ball bearings are disposed. Actuating rods 51 and 52 attached to diametrically opposed portions of ring 48 will move alternately up and down with rotation of rotary member 45. In accordance with the present invention, rods 51 and 52 are connected to the left-hand and right-hand fluid displacers 22 respectively by identical connecting rods 54. Thus, as the turbine shaft 34 rotates, the actuating rods 5l and 52 move up and down alternately raising'and lowering the respective displacers 22, as described. Since the displacers 22 are loosely fitted in the chambers 21, only a small amount `of energy is required to move them, the amount being that required to push the fluid through the conduit means 27 and regenerators 30. Since the pressure is approximately the same on both sides of the displacers 22, they can be of light construction and, hence, balancing problems are almost non-existent. The use of uid to drive the output member eliminates the problems of piston sealing required in piston-type devices and a simple mechanism as described can be utilized to drive the displacers rather than the costly crank gear and rhombic drive mechanisms heretofore required.

Since the connecting rods 54 must pass through walls defining the lower ends of chamebrs 21, suitable low friction sealing means or bushings designated as 57 are preferably provided. It has been found that by adding varying amounts of molybdenum disulfide to elastomers such as silicone rubber, natural rubber, neoprene rubber, butyl rubber, Buna N rubber, etc., an unusually satisfactory seal with a greatly reduced coefficient of friction is provided.

In choosing the liquid 36 for operating the turbine 32, it is desirable to have one that is low in viscosity and one which does not readily dissolve the gaseous operating uid in chambers 2l. It should also be noted that since the liquid 36 flows into and out of the cold ends of the chambers 21, there is little, if any, heating or vaporization problem and also the turbine housing 35 and the lower ends lof the -chambers 2l can be finned or water cooled, if necessary, to maintain the desired temperature difference between the hot and cold ends of the chambers. Enough cooling may be obtained in this manner so that the cooling fins 29 may be eliminated, if desirable.

Referring now to the embodiment illustrated schematically in FIG. 3, there is illustrated a modified form of external combustion engine generally designated by the reference numeral 60. The engine 60 is very similar in construction and operati-on to the engine 1S just described and identical reference numerals have been used to identify similar parts.

The arrangement of FIG. 13 differs from the embodiment described above in that an output member 61 comprising the turbine 32 is mounted within a sealed housing or casing 62 which is located remotely from the rest of the heat engine 60 and the liquid llines 37 and 38 are extended to supply the fluid 36 to the housing 62 to drive the turbine in its remote location. This construction offers many advantages in that it can be applied in many different applications where it `is desirable or necessary to locate the output member remotely from the main engine. One such application might be the use of a single centrally located engine to operate turbines 32 or output members located at various locations for instance at the wheels of vehicles where the engine is used to propel such vehicles, thus eliminating the need for mechanical drive mechanisms.

Another aspect shown in the embodiment of FIG. 3 which is also applicable to other embodiments is the provision of an electric generator 63 which may be partly or totally enclosed Within the turbine casing 62 preferably with the armature 64 of the generator positioned on the turbine shaft 65. This type of construction eliminates the need for high pressure rotary seals since the rings and and mechanically sealed against leakage in the walls of.

casing 62.

Another important aspect of the present invention which isequally applicable to other embodiments is the provision of independently controllable means, such as the variable speed electric motor 68 energized from generator 63 for controlling the movement of the displacers 22 at the desired speed and thus control-ling the output of the engine independently of the speed of the turbine. The prin-cipal reason for varying the relative speed of the displacers 22 is to immediately change the speed of the turbine 32. A diderence in turbine speed is needed only long enough to allow an altered'fuel input to again become matched to the mechanical output, or, in other words, -to overcome an inherent thermal lag in this type of heat engine. The moto-r 68 directly and positively controls the speed of reciprocation of the displacers independently of the output of the engine. By varying the speed of the displacers, the rate of heat absorption by 4the fworking fluid in the'chambers is changed almost immediately and this change, in turn, almost immediately effects a change in the power output of the engine. Accordingly, direct control of the reciprocation rate yof the displacers independently of the output of the engine provides a much in the position shown in FIG. 4, they pressure in the left?i 3g and valve di) int-o the right-hand chamber 21 increasing: the pressure therein.` When the pressure becomes greater in the right-hand chamber 2l than that in left-hand cham# ber 2?., reverse ilow takes place with the huid ofwing through thev right-hand passage 37 and right-hand valve more rapid response in regulation ofthe power output of the engine than is possible with a control which only regulates the amount of fuel supplied `to 4the engine. The latter control does not provide for rapid response in regulation of the engine power output because Vof the residual heat in the associated engine parts and the inherent thermal time lag caused thereby. As illustrated, theelectric motor 68 is coupled to the shaft 34 which drives the rotary member and causes members 5l and 52 to move displacers 22 in exactly the same manner as in FIGS. 1 Vand 2 of the drawings. The speed of the motor d is varied as for example by a rheostat 67 or other control device, whereby the speed of movement of the displacer-s can be regulated.

One of the major problems of previous heat engines of the yclosed type is the difficulty in control-ling the output. Heretofore, the only means available involved controlling the heat applied, such as by the valve 25. This was not satisfactory for many applications because of the time lag in response'to the variations in heat applied because of lthe residual heat capacity of the cylinder walls, etc. However, by varying the speed of reciprocation of the fluid displacers, the amount of heat absorbed by the working fluid when it is at the hot end of the chambers 2l can be accurately controlled and, hence, the output of the eng-ine can be regulated. A working fluid having a high heat conductivity, such ,as hydrogen gas, is capable of rapidly absorbing or rejecting heat and, hence, the amount of heat so absorbed or rejected is proportional to the temperature differential between the gas .and its surrounding medium and the time of vcontact of the gas with its surrounding medium. By varying this time of contact, the amount of heat absorbed or rejected can easily be controlled, almost instantaneously, over a wide range while, as previously stated, immediate and 'rapid changes in temperature of the surrounding medium or walls `are dicult to obtain because of the residual heat capacity of this medium and the time lag in response to variation of heat applied by the external .heat source.

Referring now to the embodiment illustrated schematically in FIG. 4 of the drawings, there is illustrated a heat engine 70 which is similar in many ways to the engines 18'an`d '60 previously described. Similar parts in the engine 76 are designated by the lsame reference numerals as in the previously described embodiments.

The engine 70 differs from the previously described embodiments in that no liquid is .utilized to drive the turbine wheel 32. .When the left-hand displacerv? is Vtrolled by the valve 93 (FlGS. 5, 6 and 11).

39 into the turbine casing to engage the blades 33 or" turbine 32. This fluid then returns through left-hand passage 38 and valve 49 to the left-hand'chamber 2l. This cross how of flu-id from opposite chambers is initiated in respon-se to the reciprocating movement Vof the displacer 2.2 in the respective chambers 21 with the presence in each chamber reaching its maximumwhen its respective displacer is at'or near its lowermost position.

The engine 70 is more universal in application than the other embodiments because no liquid is utilized and, hence, the engine can be mounted. Yin many different positions.

Another feature of the embodiment illustrated in FIG. 4 of the drawings, but equallyV applicable to the other embodiments, is the provision of an electric yclutch 72 positioned adjacent the turbine end of the casing designated as 73. By utilizing a `clutch of this type, high pressure rotary seals in the rturbine casing '73 can be entirelyV eliminated.

The electric clutch :schematically V.illustrated comprises a permanent magnet '74v which is secured to the turbine 32 and rotates therewith in close proximity to the interior surface of the casing "725.` Positioned to rotate in concentric relation -with-the turbine :32, but adjacent the eX- terior surfacel of the casing/73h afrotary armature 7e which is energized externally by means of the brush and slip ring connection `7*] to provide electrical energization of the windings 79 on rthe rotating armature 76. The armature 76 Ais carriedon an output shaft '78 which rotates with the turbine shaft 34y when the armature is energized. By varying the amount of energization to the windings 79, .the shaft 7S can be made to slip in a predetermined manner relative to the turbine shaft 34 and thus speed control of the output shaft 78 can readily be obtained.

In FIGS. 5 to 13, there is structurally illustrated an external combustion engine generally designated as 80 substantially like that schematically illustrated in FlGS. 1 and 2 of the drawings; As illustratedin FIGS. 5 to 13, the engine Si) is provided with a casing S1 having a flanged upper end $2 and a flanged lower end S3. Dened within the casing 81 are a pair of cylindrical chambers 8S and 86 for containin Y the compressible tluid and correspond to the chambers 21 heretofore described. Withinthe chambers there are provided loosely fitting luid displacers 37 and', respectively, like displacers 22, which reciproate to move the fluid from the upper or hot end of the chambers to the lower or cold end.

In order to provide a means for heatingthe iiuid adjacent the upper end of the chambers, there is provided a heat source means 'having a fuel line 9i which is connected to a source of fuel (not shown). The fuel line 9i supplies a plurality of downwardly and generally radially directed burners 92 which are con- The burners 92 are surrounded by an insulating cover 9d which helps to retain the heat adjacent the upper end of the chambers 85 and S6. The cover 94 is attached to the top ilange 82 by suitable means 95 and 'is provided with the necessary openings 95 to allow the combustion products toescape.

To connect the upper or hot end Vof the kchambers 35 and Sd with the lower or cold ends of these chambers there are `provi-ded conduit means generally indicated at 97 and 98, respectively (FIG. 6) which correspond to the conduit means 27 of FIGS. l and 2. The conduit means 97 and 98 include a plurality of parallel connected pairs of spirally arranged tubes 99 and 100 which communicate respectively with the upper ends of the chambers 85 and 86 through openings 101 and 102, respectively. The tubes 99 and 100 are positioned to form coils in order that heat transfer from the burners 92 to the uid within these tubes can readily be effected. The coiled tubes 99 and 100 leading from the chambers 85 and 86, respectively, terminate in a pair of heat storing devices or regenerators 105 and 106, respectively, which correspond to heat storing devices 30 of FIGS. 1 and 2.y

These regenerators 165 and 106 are disposed parallel to the chambers 85 and 86 and extend through the tianges 82 and 83. They are provided internally with finely dimensioned copper wool or the like designated as 107 in order that the fluid entering or leaving the regenerators willrapidly absorb or give up heat to the regenerator depending upon the temperature dierential between the regenerator and the fluid.

Adjacent the lower iiange 83 and attached thereto by suitable fastening means 108 is a generally cylindrical casing 110 illustrated as comprising a lower flange and an upper end wall 112, the latter abutting the lower surface of the ange 83. The casing 110 is provided with a pair of liquid containing cavities 114 and 115 which are somewhat cresent-Shaped in cross section (FIG.

8) and also a centrally disposed generally cylindrical central cavity 117.

The cavities 114, 115 are open at their lower ends and contain a non-compressible fluid, such as a liquid 119, corresponding to the fluid 36 described above. The upper end of the cavity 114 is in communication both with the lower end of regenerator 1115 and the lower end of chamber 85, the latter communication being by virtue of openings 120. Similarly the upper end of the cavity 115 is in communication with the regenerator 106 and the lower end of the chamber 86, the latter being by virtue of openings 121 (FIGS. 7 and 8). Thus, the liquid 119 in the cavity 114 is under the pressure of the working fluid in chamber 85 and the liquid in the cavity 115 is under the pressure of the working fluid in chamber 86. Preferably the outer periphery of the casing 110 is provided with cooling iins 124 which aid in cooling the working iiuid and the liquid 119 to help maintain the temperature differential between the upper and lower -ends of the chambers 85 and 86 as before described in connection with FIGS. 1 and 2.

In order to control the ow of the uid 119 to and from the lower ends of cavities 114 and 115, there is provided a iirst or upper valve plate 125 and a second or lower valve plate 126 disposed directly below the lower ange of the casing 118 and secured thereto by suitable fastening means 111. These valve plates are quite similar in many respects. The valve plate 125 in part performs the functions of valves 39 described above and similarly the valve plate 126 performs in part the functions of valves 48 described above. The valve plate 125 is provided with a plurality of radially spaced openings 127 and 128 lying on a circular line with the outer edges of the openings positioned to lie slightly inward from the outer walls dening the cavities 114 and 115. The openings 127 communicate with the cavity 114 and the openings 128 communicate with the cavity 115.

To control the fluid flow through the openings 127 and 128 and limit this iiow to the downward direction only, there are provided directly beneath the openings 127 and 128, a plurality of reed-type check valves 130 and 131, respectively, which are carried on the lower surface of the valve plate 125 (see FIG. 12). These valves correspond with the Avalves 39 in FGS. 1 and 2 and prevent liquid from flowing upwardly through the openings 127 and 128 but allow fluid to flow in the opposite direction. lThis results in a fluid flow in the general direction of the arrows as indicated in FIG. l2 of the drawings. Spaced inwardly from the openings 127 and 128 in the plate 125 are a pair of elongated arcuate shaped apertures 133 and 134. The apertures 133 is in communication with the cavity 114 and the aperture 134 is in communication with the cavity 115.

The lower valve plate 126 is similar in construction to the valve plate except that it controls flow in the opposite direction. As illustrated, it, too, is provided with generally elongated arcuate-shaped apertures 137 and 138 similar to the apertures 133 and 134 in upper valve plate 125 except for the location thereof. The aperture 137 lies directly below the openings 127 in plate 125 while the aperture 138 lie directly below the openings 128. The purpose of these apertures is to accommodate the reed-type check valves and 131, respectively, carried on the lower surface of plate 125. The plate 126 is also provided with openings 139 and 140 which lie in a circular radially spaced configuration inwardly of the apertures 137 and 138. The openings 139 lie directly below the aperture 133 in the plate 125 and the openings 148 lie directly below the aperture 134 in plate 125. The upper surface of the plate 126 is provided with a plurality of reed-type check valves 141 and 142 which are positioned above the openings 139 and 140, respectively. These valves correspond to the valves 49 in FIGS. l and 2 of the drawings and prevent the downward iiow of fluid through openings 139 and 140 while permitting an upward fiow therethrough and consequently directing the iiuid generally in the direction of the arrows indicated in FIG. 13 of the drawings. It will be appreciated that the apertures 133 and 134 in upper plate 125 are to accommodate the valves 141 and 142, respectively.

For the purpose of accurately aligning the plate 125 with the casing 110, the former is provided with an upwardly extending centrally located cylindrical boss 125:1 which houses a needle bearing 146, seal 147 and bearing retainer 148. The boss 12561 extends upwardly into the lower end of the central cavity 117 of the casing 116 thus providing the alignment feature mentioned above. The bearing 146 rotatively supports a main turbine shaft 156 corresponding with shaft 34 discussed above. Preferably shaft 150 is provided at its upper end with a portion 150e of reduced cross section which extends centrally upwardly in the cavity 117 and is supported at its upper end by a bearing 151 carried by the upper wall 112 of the casing 110.

In order to operate the displacers 87 and 88 in the manner of FIGS. 1 and 2, the shaft portion 159e drives `a member 153 preferably constructed in two parts to form a groove 154 disposed at an angle of approximately sixty degrees to the axis of shaft portion 15061. As in the schematic disclosure, the inner race of a ball bearing assembly 156 is disposed in groove 154. The outer race of the ball bearing assembly 156 supports a ring-like cam follower 158 which is provided with two diametrical op posed arms or actuating rods 159 and 160 corresponding to rods 51 and 52 of FIGS. 1 and 2. As in the schematic disclosure, the arms 159 and 160 are connetced to the lower ends of displacer rods 161 and 162 which in turn are secured to the displacers 87 and 88, respectively. The connection between the lower ends of rods 161 and 162 and arms 159 and 168, respectively, are preferably by means of ball and socket connections indicated as 164. So that the cam follower 158 does not rotate with the shaft 150, guideways 117a and 11'7b are provided in the cavity 117.

Preferably suitable sealing means or bushings 167 identical with the sealing means or bushings 57 are provided in the upper wall 112 of the casing 110, thus preventing the operating fluid from entering the `cavity 117 to any great extent. Thus, as the turbine shaft 150 is aisance For the purpose of housing a suitable turbine or drive :member for shaft G there is provided` a turbine casing` 3169 having an upper end 169e which abuts the valve plate f i126 and is'secured in position by fastening means or bolts 111. The turbine casing 169 is provided with a center cylindrical boss 15% which houses a lower needlebearing 171i,- seal 171, and retainer 172 for :supporting` the lowerl end of the turbine shaft 150. The casing 169 may also be provided with coolingns 169C for cooling purposes to helpv maintain the desired temperature diferential between the upper and lower ends of the chambers 85 and 86, as described above. 174 having a plurality of turbine blades 17d-a is housed within the casing 169 and drivingly connected to shaft 156. Directly above the turbine blades 174a there is defined in valve plate 126 an annular chamber or collector chamber 176 (FIGS. 4, 5, 9a and 13) which constitutes the interconnection or cross connection similar to 42 in FIGS. 1 and 2 of theV drawings.- The apertures 137 and 13S are interconnected at the ends as indicated at 177 (FIG. 9a) which constitutes the cross connection similar to @i1 in FIGS. 1 and 2 of the drawings.

The operation of the external combustionfengine '80 will be readily understood in view of the detailed description included above. When the displacer 87 is in the lower position, as shown in FIG. 5, pressure in the cham- -ber 5 is at or near a maximum and pressure in the chamber S6 is at or near a minimum. This pressure differential forces the liquid 119 in cavity 114 downward through the openings 127 in plate125 controlled by the reed valves 130 into-aperture 137 in plate 125. The liquid in this aperture 1.26 is directed against the turbine blades 1745i of the turbine 174 causing it to rotate. Because of collector chamber 176 this liquid has immediate access to openings 14@ in the plate 126 where it then moves upwardly through the check valves 142 and aper ture 13e-in plate 125 into the cavity 115 raising the level therein and compressing the working iiuid in the chamber 86.

Rotation of the turbine 174 causes the displacers 87 Vand 88 to reciprocate and the pressure in the chamber 86 then becomes at or near its maximum when the `displacer $8 is at its lowermost position. This causes a reversal of flow of the liquid 119 from the cavity 115 through the openings 128 in plate 12S controlled by reed valves 131 into the aperture 138 in plate 126 where it is directed y'against the blades 17451 of the turbine 174 causing it to continue its rotation in the same direction as before. The

liquid 119 travels along the pockets in the turbine 17e` adjacent the blades 174er until it reaches the openings i 139 and then it moves'upwardly past the reed valves 141 into the aperture 133 in the valve plate 125 and back into the cavity 114 raising the level therein and compressing the working uid in chamber 35. Thus, while the liquid` 119 Hows alternately back and forth between the cavities 114 and 115, the flow of liquid in the turbine is always in the same direction causing the turbine to rotate in one direction, as described.

It will be understood that the embodiment of theinvention of FIGS. 5 to 13 can be altered and changed to operate in conformance with the other embodiments and variations described and depicted in the other figures of the drawings.

While there have been shown and described several embodiments of the presentinvention, it will be apparent to those Skilled in the art that various changes and mod-i- 'cationsmay be made without departing from the invention in its broader aspects and it is, therefore, contemplated in the appended claims `to cover all such` changes and modifications as fall within the true spirit and scope of the invention.

A rotating turbine f Letters Patent of the United States is:

1.7A yheat engine comprising a kpairaof chambers containing. a' working fluid, each of said chambers having opposite ends maintained at high and low temperatures, respectively; a fiuid displacer in each chamber reeiprocally movable to displace saidfluid -betweensaid opposite ends; means for reciprocating said displacers in selected kphase relation with each other; Vand means for directly controlling the reciprocationfof said displacers at selectively adjustable rates'of reciprocation independently of the output of the engine. l

2. A heat engine comprising a pair of. chambers containing a working uid, each of said chambers having opposite ends maintained at highy and low temperatures, respectively; a liuid displacer'in each chamber reciprocally movable to displace said fluid between said opposite ends; means for reciprocating said displacers in selected phase relation with eachother; output means responsive to iiuid pressure differential between said chambersnfor converting the energy available from said pressure diterential into a useful workforce; and control means for directly controlling the reciprocation of said displacers at selectively adjustable rates of reciprocation independently of said output means.

3. Apparatus as'dened in claim 2 wherein said output means includes a rotating shaft and said control means includes mechanism controllable independently of said shaft.

4. Aheat engine comprising arpair .of chambers con'- taining a working huid, each of said chambers having opposite ends maintained at high and low temperatures,` respectively; a iiuid displacer in each chamberY reciprocally movable to displace said uid between said opposite ends; means including a iirst rotating shaft for reciprocating said `di-splacers inv selected phase relation withcach other; outv bers; and control means for directly controlling said iirst shaft to move said displ-acers at selectively adjustable rates of reciprocation. y

5. Apparatus as defined in claim 4 wherein said control means includes a variable speed electricV motor connected to said iirst shaft and a controller tor selectively adjusting the speed of said motor.

6. Apparatus vas defined in claim 5 additionally including in combination an electric generator driven by said second shaft and connected to supply electrical energy through said controller to operate said motor.

7. A hea-t engine comprising a pair of chambers containing a working fluid, each of said chambers having opposite ends maintained at high` and low temperatures, respectively; a fluid displacer in each of said chambers reciprocally movable to displace said fluid between said opposite endsgmeansfor reciprocating saidiluid displacers in selected phase relation with each other; iluid passage means linterconnecting said chambers; rotatable output means driven by iiuid pressure differential in said passage means between :said chambers; and control means for directly controlling `the reciprocation of said fluid displacers at selectively adjustable rates of reciprocation independent of the rate of rotation of said output means.

8. A heat engine comprising a pair of chambers containing a working Huid, each of said chambers having opposite ends maintained at high andlow temperatures, respectively, and arranged with at least one pair of like tem perature ends adjacent one another; a fluid displacer in each chamber reciprocally mov-abierto displace said uid between said opposite ends; casing means adjacent said one pair of ends of said chambers and in communication therewith; output means including a turbinewheel within said casing means having a ring of blades adjacent its periphery and mounted on a shaft having an output end extending externally of said casing means; said casing means including `a pair of iiuid compartments, each compartment in adsense communica-tion with one chamber end of saidvone pair of ends and in communication with a portion of the blades in said turbine wheel; first and second circular valve plates disposed between said fluid compartments and said turbine wheel, each of said valve plates defining a plurality of openings therethrough communicating between said fluid compartments and the blades of said turbine wheel; first check Valve means cooperating with s-ome of said openings permitting fiuid flow into said turbine wheel from said iiuid compartments; and second check valve means cooperating with others of said openings permitting,r fluid ow from said turbine wheel into said fluid compartments.

9. Apparatus as defined in claim 8 wherein said check valve means includes a plurality of reed valves arranged in circular configuration on said valve plates, some of said valves operable in response to fluid pressure in said compa-rtments to direct fluid against the blades of said turbine wheel.

10. Apparatus as defined in claim 8 wherein each of said valve plates includes at least one opening formed in a circular arcuate shape arranged about a central axis and a plurality of holes arranged in circular configuration concentric to said axis and adjacent each of said arcuate openings, and wherein said check valve means are positioned in the arcuate opening of one plate for cooperation with said holes in the other plate to control the iiuid iow toward and away from said turbine.

11. Apparatus as defined in claim 8 including a pair of heat storage devices, each of said devices comprising i4 a housing containing a highly heat conductive, finely divided material, each of said housings in communication between one of said fiuid compartments in said casing and one end of the other pairs of like temperature ends of said chambers.

12. Apparatus as defined in claim 11 including a heat source adjacent one pair of like temperature ends of said chambers and wherein each of said heat storage devices includes heating coil means adjacent said heat source in communication between said housing .and said one of the other pairs of like temperature ends of said chambers.

References Cited by the Examiner UNiTED STATES PATENTS 674,872 5/01 Nixon 260-765 1,290,756 1/ 19 Kasley 60-24 1,600,734 9/26 Koenig 60-24 1,614,962 1/27 Koenig 60-24 2,272,925 2/ 42 Smith 62-6 X 2,276,520 3/ 42 Stapelfeld 260-765 2,486,081 10/ 49 Van Weenan 60--24 X 2,579,702 12/5 i Rinia et al 60-24 2,643,508 6/53 Clay et al 60-24 2,657,527 11/53 Muller et al 60-24 IULIUS E. WEST, Primary Examiner.

EDGAR W. GEGGHEGAN, Examiner. 

1. A HEAT ENGINE COMPRISING A PAIR OF CHAMBERS CONTAINING A WORKING FLUID, EACH OF SAID CHAMBERS HAVING OPPOSITE ENDS MAINTAINED AT HIGH AND LOW TEMPERATURES, RESPECTIVELY; A FLUID DISPLACER IN EACH CHAMBER RECIPROCALLY MOVABLE TO DISPLACE SAID FLUID BETWEEN SAID OPPOSITE ENDS; MEANS FOR RECIPROCATING SAID DISPLACERS IN SELECTED PHASE RELATION WITH EACH OTHER; AND MEANS FOR DIRECTLY CONTROLLING THE RECIPROCATION OF SAID DISPLACERS AT SELECTIVELY ADJUSTABLE RATES OF RECIPROCATION INDEPENDENTLY OF THE OUTPUT OF THE ENGINE. 